EP4388210A1 - Élément de fixation fileté - Google Patents

Élément de fixation fileté

Info

Publication number
EP4388210A1
EP4388210A1 EP22859100.4A EP22859100A EP4388210A1 EP 4388210 A1 EP4388210 A1 EP 4388210A1 EP 22859100 A EP22859100 A EP 22859100A EP 4388210 A1 EP4388210 A1 EP 4388210A1
Authority
EP
European Patent Office
Prior art keywords
threaded fastener
nut
recesses
threaded
positioner
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22859100.4A
Other languages
German (de)
English (en)
Other versions
EP4388210A4 (fr
Inventor
Brian C. Ford
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Amsted Rail Co Inc
Original Assignee
Amsted Rail Co Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Amsted Rail Co Inc filed Critical Amsted Rail Co Inc
Publication of EP4388210A1 publication Critical patent/EP4388210A1/fr
Publication of EP4388210A4 publication Critical patent/EP4388210A4/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/02—Locking of screws, bolts or nuts in which the locking takes place after screwing down
    • F16B39/10—Locking of screws, bolts or nuts in which the locking takes place after screwing down by a plate, spring, wire or ring immovable with regard to the bolt or object and mainly perpendicular to the axis of the bolt
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/02—Locking of screws, bolts or nuts in which the locking takes place after screwing down
    • F16B39/04—Locking of screws, bolts or nuts in which the locking takes place after screwing down with a member penetrating the screw-threaded surface of at least one part, e.g. a pin, a wedge, cotter-pin, screw
    • F16B39/06—Locking of screws, bolts or nuts in which the locking takes place after screwing down with a member penetrating the screw-threaded surface of at least one part, e.g. a pin, a wedge, cotter-pin, screw with a pin or staple parallel to the bolt axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B21/00—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings
    • F16B21/10—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts
    • F16B21/16—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft
    • F16B21/18—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details
    • F16B21/183—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details internal, i.e. with spreading action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B21/00—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings
    • F16B21/10—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts
    • F16B21/16—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft
    • F16B21/18—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details
    • F16B21/186—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details external, i.e. with contracting action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B37/00—Nuts or like thread-engaging members
    • F16B37/04—Devices for fastening nuts to surfaces, e.g. sheets, plates
    • F16B37/041—Releasable devices

Definitions

  • a nut is a piece of hardware that may be threaded onto an axle or spindle to secure a wheel. When installing, the correct torque should be applied to the nut to maximize bearing life and to ensure that the axle nut will not loosen over time.
  • the present embodiments include a threaded fastener that may be used in any application that uses nuts and similar types of threaded fasteners.
  • the threaded fastener may be used as an axle nut to secure components on a threaded spindle.
  • the threaded fastener may be constructed using readily available commercial components, and can easily lock into place to prevent movement of a wheel bearing.
  • the threaded fastener is easily removable for service and unitized (i.e., has components that are physically connected to form a single part) to prevent components from separating and to prevent tampering with the threaded fastener, wheel bearing, or both.
  • FIG. 1 is an exploded view of a threaded fastener that affixes to a threaded spindle, in an embodiment.
  • FIG. 2 is a perspective view of a positioner of the threaded fastener of FIG. 1, in an embodiment.
  • FIG. 3 is a cross-sectional view of the threaded fastener of FIG. 1 showing a contact engaged with a recess, in an embodiment.
  • FIG. 5 is a side cutaway view of the threaded fastener of FIG. 1, in an embodiment.
  • FIG. 6 is a top view of the threaded fastener of FIG. 1 illustrating azimuthal positioning of plungers about a rotation axis, in an embodiment.
  • FIG. 7 is a cross-sectional view of the threaded fastener of FIG. 1 showing an indentation cooperating with a retaining ring to axially constrain the positioner, in an embodiment.
  • FIG. 8 is a cross-sectional view showing the threaded fastener of FIG. 1 with another embodiment of the retaining ring.
  • FIG. 9 is a cutaway view of a threaded fastener that is similar to the threaded fastener of FIG. 1 except that it uses a positioner shaped as an undulating wire to create a plurality of recesses, in an embodiment.
  • FIG. 10 shows the positioner of FIG. 9 in more detail, in an embodiment.
  • FIG. 11 is a side cutaway view of the threaded fastener of FIG. 9 that illustrates a circumferential gap in more detail, in an embodiment.
  • FIG. 1 is an exploded view of a threaded fastener 100 that affixes to a threaded spindle 108.
  • the threaded fastener 100 includes a nut 102 forming a threaded central hole 122 that is threaded to match external threads 126 of the spindle 108.
  • the threaded central hole 122 and spindle 108 are coaxial to a rotation axis 124 about which the nut 102 rotates, and along which the nut 102 linearly translates, or advances, to engage with the external threads 126 of the spindle 108.
  • rotation axis 124 coincides with the z axis of a right-handed Cartesian coordinate system 120, wherein the nut 102 translates in the -z direction when engaging with the spindle 108, and in the +z direction when disengaging from the spindle 108.
  • FIG. 2 is a perspective view of a positioner 104 of the threaded fastener 100.
  • the positioner 104 is shaped as a disc 148 that lies flat in the x-y plane and forms an unthreaded central hole 134 through which the spindle 108 passes.
  • the disc 148 also forms a sequence of recesses 114 located circumferentially around the unthreaded central hole 134.
  • Extending axially upward (i.e., along the +z direction) from an outer edge of the disc 148 is a lip 146.
  • the lip 146 forms a plurality of indentations 138 that can be pushed radially inward to unitize the threaded fastener 100.
  • the disc 148 forms a tab 136 that extends radially inward to engage with a vertical slot 118 formed by the spindle 108.
  • the tab 136 and slot 118 cooperatively prevent the positioner 104 from rotating about the rotation axis 124. It is assumed herein that the slot 118 is located in the +y direction relative the rotation axis 124. Thus, when the positioner 104 is engaged with the spindle 108, the tab 136 will be located in the slot 118, and therefore also located in the +y direction relative to the rotation axis 124.
  • affixed to the nut 102 circumferentially around the threaded central hole 122 are a plurality of spring plungers 106 that engage with the recesses 114.
  • the plungers 106 cooperate with the recesses 114 to create a detent mechanism that both arrests motion of the nut 102 while it is being tightened onto the spindle 108 and divides rotation of the nut 102 into discrete angular increments about the rotation axis 124.
  • the nut 102 forms a first plunger mounting hole 112(1) and a second plunger mounting hole 112(2) that receive the first plunger 106(1) and the second plunger 106(2), respectively.
  • the threaded fastener 100 may have only one plunger 106, or more than two plungers 106 (and corresponding plunger mounting holes 112) without departing from the scope hereof.
  • One advantage of the threaded fastener 100 is that all of the plunger mounting holes 112 can be drilled into one axial end of the nut 102.
  • the nut 102 only needs to be mounted one time to a fixture (e.g., a vise) for drilling all of the plunger mounting holes 112.
  • the nut 102 can be made from a process such as metal injection molding (MIM). Since the plunger mounting holes 112 have axes that are parallel to each other (and parallel to the rotation axis 124), the nut 102 can be pulled off of the MIM tooling in a single direction, drastically reducing manufacturing complexity.
  • MIM metal injection molding
  • plunger mounting holes drilled radially through the nut 102 would require the nut 102 to be rotated and remounted for each hole.
  • all of the recesses 114 can be advantageously drilled into one side of the disc 148 of the positioner 104.
  • FIGS. 3 and 4 are cross-sectional views of the fastener 100 when threaded onto the spindle 108.
  • FIGS. 3 and 4 depict operation of the fastener 100 after it has been advanced along the spindle 108 such that the positioner 104 contacts an end face 110 of the spindle 108, i.e., the axial position of the positioner 104 is fixed by the end face 110.
  • a bottom face 232 of the nut 102 is axially separated (i.e., along the z direction) from a top face 234 of the positioner 104 by a gap 244.
  • the nut 102 may be torqued (e.g., by a wrench) to either tighten or loosen the fastener 100.
  • the nut 102 advances toward the positioner 104 (i.e., in the -z direction), thereby reducing the gap 244.
  • the fastener 100 may be tightened to a predetermined torque level (e.g., by a torque wrench) or such that it “bottoms out” when the bottom face 232 directly contacts the top face 234.
  • a torque wrench e.g., a torque wrench
  • the nut 102 advances away from the positioner 104 (i.e., in the +z direction), thereby increasing the gap 244.
  • FIGS. 3 and 4 are best viewed together with the following description.
  • FIGS. 3 and 4 The cross-sectional views of FIGS. 3 and 4 are taken through the rotation axis 124 and a plunger 206 which may be any one of the plungers 106 in FIG. 1.
  • the plunger 206 has a cylindrical shaft 216 with a plunger axis 226 that is parallel to the rotation axis 124 and transversely displaced from the rotation axis 124 (i.e., in the x-y plane) by a radial distance R.
  • the plunger 206 is inserted into a plunger mounting hole 212 which may be any one of the plunger mounting holes 112 in FIG. 1.
  • the plunger mounting hole 212 may be a straight unthreaded through-hole or blind hole into which the plunger 106 is inserted and affixed via an interference fit.
  • the plunger 106 may be inserted into the plunger mounting hole 212 and affixed thereto via epoxy.
  • the plunger mounting hole 212 may be threaded to accept external threads of the cylindrical shaft 216, in which case the plunger 206 is threaded into the plunger mounting hole 212.
  • the plunger 106 may inserted into, and affixed to, the plunger mounting hole 212 using another mounting mechanism without departing from the scope hereof.
  • the plunger 206 also has a contact 218 affixed to the bottom of a spring 228 that extends and compresses along the plunger axis (i.e., the z direction).
  • the top of the spring 228 is fixed to the shaft 216, and therefore the spring 228 exerts an axial force against the contact 218, thereby pushing the contact 218 downward.
  • the contact 218 is shaped to engage with each of the recesses 114 when positioned thereover.
  • the contact 218 is shaped as a sphere (e.g., a ball bearing).
  • the contact 218 may be a pin with a curved bottom face (e.g., a bullnose).
  • the contact 218 may be another type of mechanism that is actuated via the spring 228 to engage with the recesses 114.
  • the recess 214 may alternatively be a blind hole.
  • the recess 214 may be shaped as an untruncated right circular cone.
  • the recess 214 may be a straight through hole or blind hole, or a counterbored hole.
  • the recess 214 may have a different shape than shown herein and need not be cylindrical or conical.
  • the azimuthal angle 6 is 174.375°.
  • the plunger mounting holes 112(1) and 112(2) may be alternatively positioned to form a different azimuthal angle 6 such that the second plunger 106(2) is positioned between a different pair of neighboring recesses 114 when the first plunger 106(1) engages with one of the recesses 114.
  • the azimuthal angle 6 is 180° and the number of recesses 114 is odd. In this case, no two of the recesses 114 are azimuthally separated by 180°, thereby ensuring that the plungers 106(1) and 106(2) do not simultaneously engage with two of the recesses 114.
  • the threaded fastener 100 may be designed such that two or more plungers 106 simultaneously engage with two or more recesses 114.
  • Each of the two or more plungers 106 may be centered at the same radial distance R from the rotation axis 124. In this case, the torque and energy required to disengage the two or more plungers 106 scales with the number of plungers 106 that are simultaneously engaged with the recesses 114.
  • the retaining ring 710 is axially constrained between the disc 148 and the indentations 138, and thus the nut 102 and positioner 104 are unitized.
  • the term “unitized” means that the nut 102 cannot be separated from the positioner 104, however the nut 102 can still freely rotate with respect to the positioner 104.
  • “freely rotate” means that the retaining ring 710 does not force the positioner 104 against the plungers 106(1) and 106(2) (i.e., the plungers 106(1) and 106(2) are not pre-loaded by the positioner 104).
  • the threaded fastener 100 need not be unitized, in which case the retaining ring 710 may be excluded. Accordingly, one of the present embodiments includes only the nut 102 and plungers 112, in which case the positioner 104 may be provided by a third party. Another of the present embodiments includes only the positioner 104, in which case the nut 102 and plungers 112 may be provided by a third party.
  • FIG. 9 is a cutaway view of a threaded fastener 900 that is similar to the threaded fastener 100 of FIGS. 1-8 except that it uses a positioner 904 shaped as an undulating wire to create a plurality of recesses.
  • the threaded fastener 900 as compared to the threaded fastener 100, may be easier to assemble, thereby reducing cost.
  • the threaded fastener 900 includes a nut 902 that is similar to the nut 102 of FIG. 1 except that it includes a lip 908 that extends axially upward from a top face 924 of the nut 902 and continuously surrounds the rotation axis 124.
  • the nut 902 has a bottom face 916 that contacts the end face 110 of the spindle 108 when the fastener 900 is tightened thereon.
  • the lip 908 forms a circumferential gap 914 that also continuously encircles the rotational axis 124 and within which at least part of the positioner 904 is placed (see FIG. 11).
  • the threaded fastener 900 includes a retaining ring 910 that is at least partially inserted into the gap 914 to axially constrain the positioner 904 relative to the top face 924.
  • FIG. 10 shows the positioner 904 in more detail.
  • the positioner 904 is a wire forming at least part of a loop encircling the rotational axis.
  • the wire additionally forms a plurality of radial undulations that define a plurality of recesses 1014. Specifically, each radial undulation defines one of the recesses 1014. Due to the radial undulations, the recesses 1014 alternate between opening radially inward and opening radially outward.
  • the recesses 1014 will be uniformly spaced about the rotation axis 124 (i.e., azimuthally in the transverse x-y plane) and all located the same radial distance from the rotation axis 124. While FIG. 10 shows the positioner 904 with 24 radial undulations forming 24 recesses 1014, the positioner 904 may be alternatively shaped with a different number of radial undulations without departing from the scope hereof.
  • one end of the wire is bent radially inward to form a tab 1020 that engages with the vertical slot 118 of the threaded spindle 108 to rotationally constrain the positioner 904.
  • the tab 1020 may additionally include one or both of an axial leg 1016 and a transverse leg 1018 to improve how snugly the tab 1020 fits into the slot 118.
  • FIG. 11 is a side cutaway view of the threaded fastener 900 that illustrates the circumferential gap 914 in more detail.
  • the circumferential gap 914 is formed radially outward from a radial inward-facing surface 1104 of the lip 908.
  • the circumferential gap 914 has a rectangular cross section defined by a radial extent 1106 and an axial extent 1102.
  • the top face 924 of the nut 902 forms the bottom wall of the circumferential gap 914.
  • at least part of the positioner 904 and retaining ring 910 are positioned inside the circumferential gap 914.
  • the circumferential gap 914 may have a different cross-sectional shape and size than shown in FIGS. 9 and 11 without departing from the scope hereof.
  • the threaded fastener 900 also includes a first plunger 906(1) and a second plunger 906(2) that are similar to the first plunger 106(1) and second plunger 106(2), respectively, of FIG. 1. However, each of the plungers 906(1) and 906(2) is oriented such that its contact 218 moves axially upward to engage with the recesses 1014.
  • the size and geometry of the circumferential gap 914 pre-load each of the plungers 906(1) and 906(2) with a pre-loading force when said each of the plungers 906(1) and 906(2) is engaged with a corresponding recess 1014.
  • a tightening torque is the minimum torque that must applied to the nut 902 to disengage one of the plungers 906(1) and 906(2) from a recess 1014. Due to the pre-loading force, the nut 902 does not freely rotate with respect to the retaining ring 910 and positioner 904.
  • the fastener 900 Since the pre-loading force and tightening torque are fixed by the geometry and configuration of the fastener 900, they do not change as the fastener 900 is threaded along the spindle 108. As a result, the fastener 900 behaves differently than the fastener 100 of FIGS. 1-8 in that the fastener 900 always clicks as it rotates, regardless of its axial position along the spindle 108. Thus, the plungers 906(1) and 906(2) are always engaging and disengaging with the recesses 1014, even when the fastener 900 is not contacting the end face 110.
  • the plungers 106(1) and 106(2) of the fastener 100 are not pre-loaded, and therefore the positioner 104 will be “loose” relative to the nut 102. Only when the fastener 100 approaches the end face 110 (e.g., within one turn of the nut 102) will the positioner 104 apply a force against the plungers 106(1) and 106(2) such that the plungers 106(1) and 106(2) begin to engage and disengage with the recesses 114 (i.e., produce clicks).
  • fastener 900 Another difference between the fastener 900 and the fastener 100 is that the tightening torque does not increase as the fastener 900 is tightened against the end face 110. Specifically, an increase in torque applied to the nut 902 does not result in a larger force exerted against the plungers 906(1) and 906(2), and therefore the same back-off torque can loosen the nut 902 no matter how much the nut 902 was tightened.
  • the fastener 100 behaves more like a conventional washer in that it transfers the tightening torque into an axial locking force that pushes the internal threads of the central hole 122 against the external threads 126 of the spindle 108. Accordingly, as the tightening torque is increased, the magnitude of this locking force also increases, as does the back-off torque needed to loosen the nut 102.
  • the recesses 1014 of the threaded fastener 900 are axially located toward the top of the nut.
  • the plungers 906(1) and 906(2) are oriented opposite to the plungers 106(1) and 106(2).
  • This orientation increases the contact surface area between the nut 902 and the end face 110.
  • the fastener 900 can be alternatively threaded onto the spindle 108 in the opposite manner, i.e., with the lip 908 facing and contacting the end face 110.
  • this alternative orientation may not always be feasible given the smaller contact area of the lip 908.
  • a threaded fastener includes a nut forming a threaded center hole that defines a rotational axis of the threaded fastener.
  • the threaded fastener also includes a plurality of spring plungers affixed to the nut, each of the plurality of spring plungers including a shaft that is aligned parallel to the rotational axis.
  • the threaded faster also includes a positioner forming (i) an unthreaded center hole that is coaxial with the threaded center hole and (ii) a plurality of recesses facing the plurality of spring plungers. At least one of the plurality of spring plungers engages with a corresponding at least one of the plurality of recesses when the nut is tightened against the positioner on a threaded spindle.
  • each of the plurality of spring plungers includes a spring that exerts an axial force against a contact to push the contact against the positioner.
  • the nut forms a plurality of plunger mounting holes surrounding the threaded center hole.
  • Each of the plurality of spring plungers is inserted into a corresponding one of the plurality of plunger mounting holes.
  • each of the plurality of plunger mounting holes is centered at an identical radius from the rotational axis.
  • each of the plurality of recesses is centered at the identical radius from the rotational axis.
  • the nut is shaped as a polygon.
  • each of the plurality of spring plungers is located at a corresponding corner of the nut.
  • the threaded fastener further includes a retaining ring that encircles the nut about the rotational axis.
  • the positioner includes (i) a disc forming the unthreaded center hole and the plurality of recesses and (ii) a lip extending axially upward from an outer edge of the disc and forming indentations that extend radially inward from the outer edge. The indentations cooperate with the retaining ring to axially constrain the positioner relative to the nut.
  • the retaining ring includes a flange integrally formed with the nut and extending radially outwards from outer-facing surfaces of the nut.
  • the retaining ring includes an annulus inserted into a plurality of notches, formed in outer-facing surfaces of the nut, that axially constrain the annulus.
  • each of the plurality of recesses being one of a countersunk hole, a counterbored hole, and a straight through-hole.
  • the positioner includes a wire forming at least part of a loop encircling the rotational axis, the wire additionally forming a plurality of radial undulations that define the plurality of recesses.
  • the nut in the threaded fastener denoted (Al 6), the nut includes a lip that (i) extends circumferentially around the threaded center hole, (ii) extends axially away from a top face of the nut, and (iii) has a radially inward-facing surface that forms a circumferential gap.
  • the threaded fastener further includes a retaining ring inserted into the circumferential gap to axially constrain the wire relative to the top face of the nut.
  • the wire has a first end extending radially inward to form a tab that engages with a slot of the threaded spindle to rotationally constrain the wire relative to the threaded spindle.
  • the plurality of spring plungers and the plurality of recesses are angularly spaced about the rotational axis such that two or more of the plurality of spring plungers simultaneously engage with two or more of the plurality of recesses.
  • the plurality of spring plungers are uniformly spaced about the rotational axis by a plunger angular spacing
  • the plurality of recesses are uniformly spaced about the rotational axis by a recess angular spacing
  • the plunger angular spacing is not an integer multiple of the recess angular spacing.
  • a number of the plurality of recesses is not an integer multiple of a number of the plurality of spring plungers.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)

Abstract

Un élément de fixation fileté comprend un écrou formant un trou central fileté qui définit un axe de rotation. L'élément de fixation fileté comprend également une pluralité de poussoirs à ressort fixés à l'écrou, chacun d'eux comprenant un arbre qui est aligné parallèlement à l'axe de rotation. L'élément de fixation fileté comprend également un positionneur formant (i) un trou central non fileté qui est coaxial avec le trou central fileté et (ii) une pluralité d'évidements faisant face aux poussoirs à ressort. Lorsque l'écrou est couplé contre le positionneur sur une broche filetée, les poussoirs à ressort solidarisent et désolidarisent de manière répétée les évidements lorsque l'écrou tourne relativement au positionneur. Les évidements sont formés de telle sorte que le positionneur convertit le couple appliqué en une force linéaire qui comprime les poussoirs à ressort, verrouillant ainsi les filets de l'écrou contre les filets de la broche.
EP22859100.4A 2021-08-18 2022-08-17 Élément de fixation fileté Pending EP4388210A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US17/406,000 US12241495B2 (en) 2021-08-18 2021-08-18 Threaded fastener
PCT/US2022/040585 WO2023023145A1 (fr) 2021-08-18 2022-08-17 Élément de fixation fileté

Publications (2)

Publication Number Publication Date
EP4388210A1 true EP4388210A1 (fr) 2024-06-26
EP4388210A4 EP4388210A4 (fr) 2025-05-07

Family

ID=85228613

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22859100.4A Pending EP4388210A4 (fr) 2021-08-18 2022-08-17 Élément de fixation fileté

Country Status (5)

Country Link
US (1) US12241495B2 (fr)
EP (1) EP4388210A4 (fr)
CN (1) CN118251552A (fr)
CA (1) CA3227571A1 (fr)
WO (1) WO2023023145A1 (fr)

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US12241495B2 (en) 2025-03-04
EP4388210A4 (fr) 2025-05-07
WO2023023145A1 (fr) 2023-02-23
CN118251552A (zh) 2024-06-25
CA3227571A1 (fr) 2023-02-23
US20230060078A1 (en) 2023-02-23

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